US5669223A - Transport temperature control system having enhanced low ambient heat capacity - Google Patents

Transport temperature control system having enhanced low ambient heat capacity Download PDF

Info

Publication number
US5669223A
US5669223A US08/665,968 US66596896A US5669223A US 5669223 A US5669223 A US 5669223A US 66596896 A US66596896 A US 66596896A US 5669223 A US5669223 A US 5669223A
Authority
US
United States
Prior art keywords
expansion valve
outlet
evaporator
compressor
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/665,968
Other languages
English (en)
Inventor
James H. Haley
Gillian M. Drake
Doyle G. Herrig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thermo King Corp
Original Assignee
Thermo King Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thermo King Corp filed Critical Thermo King Corp
Priority to US08/665,968 priority Critical patent/US5669223A/en
Application granted granted Critical
Publication of US5669223A publication Critical patent/US5669223A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H1/00899—Controlling the flow of liquid in a heat pump system
    • B60H1/00907—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant changes and an evaporator becomes condenser
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/323—Cooling devices using compression characterised by comprising auxiliary or multiple systems, e.g. plurality of evaporators, or by involving auxiliary cooling devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D29/00—Arrangement or mounting of control or safety devices
    • F25D29/003—Arrangement or mounting of control or safety devices for movable devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00942—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a plurality of heat exchangers, e.g. for multi zone heating or cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00957—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising locations with heat exchange within the refrigerant circuit itself, e.g. cross-, counter-, or parallel heat exchange
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms

Definitions

  • the invention relates in general to transport temperature control systems, and more particularly to systems having heating and cooling cycles which enhance the capacity for heating a served space during low ambient temperature conditions.
  • Transport temperature control systems operate in both a cooling and heating capacity to provide the necessary environment for a served space, such as a truck or trailer box section.
  • the system switches between the cooling and heating modes of operation by means of a mode selector valve.
  • a mode selector valve In a first or cooling circuit, hot compressor discharge gas is fed in series to a condenser, a receiver, a heat exchanger, an expansion valve, evaporator, an accumulator and is returned to the compressor.
  • the mode selector valve diverts the hot compressor discharge gas to an evaporator defrost pan heater, the evaporator, the heat exchanger, accumulator and returns to the compressor.
  • prior art procedures provide a means for pressurizing the receiver with the hot compressor discharge gas to force liquid refrigerant from the receiver and into the refrigerant circuit.
  • a bleed port is provided in the expansion valve to allow this liquid refrigerant to flow into the evaporator during the heating cycle to improve heating or defrost capacity.
  • An example of such a system is U.S. Pat. No. 4,419,866. Improvements on this type of operation can also be found in U.S. Pat. Nos. 4,748,818, 4,912,933 and 5,056,324, all of which are assigned to the present assignee and hereby incorporated herein by reference.
  • the accumulator may also be heated to change the liquid refrigerant to a gas to increase heating capacity.
  • the condenser is flooded in order to increase the pressure in the system such that additional refrigerant is added to the system during the heating cycle.
  • This has several disadvantages. Some of these are that a larger charge of refrigerant is required to provide the increase in pressure, shutters are needed to restrict the air flow around the condenser during cold ambients to minimize the amount two-phase refrigerant present in the condenser, or condenser fan contacts and controls are needed to shut off the fan for minimal condenser air flow.
  • Each of these schemes requires increased system complexity, and hence increased cost for the unit.
  • the desired result is high heat capacity at all ambient temperatures without returning liquid refrigerant to the compressor.
  • An excess amount of liquid refrigerant leaving the accumulator can enter the compressor and cause failure of compressor components. Therefore, it is desirable that superheated vapor be returned to the compressor.
  • the accumulator is a two phase device that must return a minimum amount of liquid to the compressor for lubrication oil return for compressor components.
  • the refrigerant mixture leaving the accumulator is most preferably above saturation temperature.
  • a system and method are needed that will control the amount of refrigerant flow so that the maximum quantity of superheated gas and liquid oil are returned to the compressor at all ambient temperatures.
  • a transport temperature control system having cooling and heating cycles, a first refrigerant circuit which includes a compressor, condenser, receiver, first expansion valve, and evaporator, a second refrigerant circuit which includes the compressor and evaporator, and mode selector means having cooling and heating output ports selectively connectable to the first and second refrigerant circuits, respectively.
  • the improvement comprises a second expansion valve having its inlet connected between the receiver and an inlet to the first expansion valve, an outlet connected between the evaporator and the compressor and sensing means for sensing a superheat condition of the refrigerant at a location between the evaporator and the compressor.
  • the second expansion valve means operates to moderate the level of superheat of the refrigerant passed to the compressor to permit more efficient compressor operation.
  • the second sensing means is located a point upstream of the outlet of the second expansion valve, such that the opening of said second expansion valve means is controlled according to a predetermined level of the superheat condition.
  • FIG. 1 is a schematic diagram of a preferred embodiment of a transport temperature control system according to the present.
  • FIG. 2 is a schematic diagram of a second embodiment of a transport temperature control system according to the present.
  • the refrigeration system is mounted, for example, on the front wall 13 of a truck or trailer.
  • the refrigeration system includes a closed refrigeration circuit 16 which includes a refrigerant compressor 19 driven by a prime mover, such as an internal combustion engine (not shown).
  • Discharge ports 22 of the compressor 19 are connected to an inlet port 25 of a three-way valve 28 via a discharge service valve 31 and hot gas conduit or line 34.
  • the functions of the three-way valve 28, which has a heating and a cooling position, may be provided by separate valves, if desired.
  • a first refrigeration circuit 37 the three-way valve 28 is placed in the cooling position (not shown), and one of the outlet ports 40 connected to an inlet side 43 of a condenser coil 46.
  • An outlet side 49 of the condenser is connected to an inlet side 52 of a receiver tank 55, which includes an outlet side 58 which may also include a service valve 61.
  • a one-way check valve 64 may be placed in the refrigerant line just prior to the receiver tank 55. From the receiver tank, high pressure liquid refrigerant passes along a conduit 67 and through a coil 70 in a heat exchanger 73, via a drier 76, to a first expansion valve 79.
  • a second one-way check valve 82 is placed in the refrigerant line between an outlet 85 of the heat exchanger coil 70 and the inlet 88 of the first expansion valve 79.
  • the outlet 91 of the expansion valve is connected to a distributor 92 which distributes low pressure liquid refrigerant to inlets on the inlet side 94 of an evaporator coil 97.
  • the outlet side 100 of the evaporator coil is connected to the inlet side 103 of a closed accumulator tank 106 via passage through the heat exchanger 73.
  • the first expansion valve 79 is controlled by an expansion valve thermal bulb 109 and evaporator outlet pressure.
  • Low pressure gaseous refrigerant in the accumulator tank 106 is directed from the outlet side 115 thereof to the suction port 118 of the compressor 19 via suction line 121, suction service valve 124, and an optional suction throttling valve (not shown).
  • a portion of a liquid mixture 127 (generally lubrication oil) is passed from the accumulator 106 to the compressor 19, for purposes of lubrication of compressor components, which function will be described more fully in discussion of the heating mode of the present invention.
  • a hot gas line 130 extends from the second outlet port 133 of three-way valve to the inlet side 94 of the evaporator coil 77 via an optional defrost pan heater 136 located below the evaporator coil.
  • the heating position of three-way valve diverts the hot, high pressure refrigerant gas from the compressor 19 of the first refrigerant circuit 37, into a second, or heating mode, refrigerant circuit 139.
  • the second refrigerant circuit includes the hot gas conduit or line 130, defrost pan heater 136, the distributor 84, and the evaporator coil 97.
  • the first expansion valve 79 is bypassed during the heating mode.
  • the one-way check valve 82 prevents any migration of refrigerant from the first expansion valve 79 back to the receiver tank 55 during low ambients. If the heating mode is initiated by a defrost cycle, by an appropriate control method, an evaporator fan (not shown) is not operated, or if the fan remains operative, an air damper (not shown) is closed to prevent warm air from being delivered to the served space 142. During a heating cycle required to hold a thermostat set point temperature, the evaporator fan is operated and the air damper remains open. After the evaporator 97, the liquid mixture, low pressure refrigerant gas and oil, passes to the heat exchanger 73, accumulator 106 and back to the compressor 19, as in the cooling mode.
  • a second expansion valve 145 is operably connected to the system 16 to meter the refrigerant flow under low ambient operating conditions so that refrigerant gas is returned to the compressor 19 at all ambient temperatures, while permitting refrigerant flow from the receiver 55 and condenser 46 during low ambients, thus providing for the required heating capacity at all ambient conditions.
  • flow through the second expansion valve is restricted or closed off, while at low ambients, more refrigerant flows through the valve into the system.
  • an inlet line 148 of the second expansion valve 145 is connected to the second 139 circuit at a point between the drier 76 and the first expansion valve inlet 88, and preferably at a location between the heat exchanger outlet 85 and the first expansion valve inlet.
  • the inlet 148 of the second expansion valve 145 can be connected to the liquid refrigerant line 67 at any point upstream of the first expansion valve 79.
  • the outlet 151 of the second expansion valve is connected to the second refrigerant circuit at a location between the evaporator outlet 100 and the compressor, preferably at the accumulator inlet 103, and most preferably at a point just prior to the heat exchanger 73, as shown in FIG. 1.
  • the sensor bulb 154 of the second expansion valve is preferably located downstream of the evaporator 97 and anywhere prior to the compressor 19.
  • the second expansion valve sensor bulb is located at a point upstream of the second expansion valve outlet. If the superheat of the refrigerant leaving the evaporator is above acceptable limits, the second expansion valve 145 will open to allow refrigerant to pass from the conduit 67, since the receiver has a higher pressure than that at the evaporator outlet 100 (or the compressor inlet).
  • the degree of opening of the second expansion valve is controlled such that it is fully open when the superheat condition is above about 40° F., and fully closed when the superheat condition is below about 20° F.
  • heating capacity is optimized while also ensuring that a minimal level of liquid mixture 127 is passed to the compressor 19 for adequate component lubrication.
  • the sensor bulb 154 of the second expansion valve is placed downstream of the outlet 151.
  • the sensor 154 senses the superheat of the refrigerant leaving the evaporator 97 after it has been moderated by the additional refrigerant gas admitted from the high side conduit 67.
  • This type of arrangement prevents too much refrigerant from being added to the system such that the superheat level of the refrigerant is above acceptable limits which may allow liquid refrigerant to be passed to the compressor 19, which would otherwise have the potential to cause failure of compressor components.
  • This arrangement assures that the moderated superheat level of the refrigerant passing through the heat exchanger 73 is of sufficient superheat so that the correct level of gaseous refrigerant is passed to the compressor for enhanced heating.
  • An additional advantage of the present invention is that it may energize during the first or cooling cycle. If the evaporator outlet 100 has a superheat which is above normal cooling levels, then the second expansion valve 145 will feed additional refrigerant to the circuit. During moderate ambient, low box 142 (served space) temperature operating conditions, it is possible for the refrigerant to have too high of a superheat as it exits the evaporator 97. If the ambient temperature is moderate, the condenser pressure is not sufficient to force enough liquid across the thermal expansion valve 79.
  • the second expansion valve 145 is energized, thereby creating another circuit for the refrigerant to enter the low side from the higher pressure side, when too high a superheat is sensed by the sensing bulb 154, to moderate the superheat entering the compressor 19.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
US08/665,968 1995-02-08 1996-06-21 Transport temperature control system having enhanced low ambient heat capacity Expired - Fee Related US5669223A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08/665,968 US5669223A (en) 1995-02-08 1996-06-21 Transport temperature control system having enhanced low ambient heat capacity

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US38549995A 1995-02-08 1995-02-08
US08/665,968 US5669223A (en) 1995-02-08 1996-06-21 Transport temperature control system having enhanced low ambient heat capacity

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US38549995A Continuation 1995-02-08 1995-02-08

Publications (1)

Publication Number Publication Date
US5669223A true US5669223A (en) 1997-09-23

Family

ID=23521636

Family Applications (1)

Application Number Title Priority Date Filing Date
US08/665,968 Expired - Fee Related US5669223A (en) 1995-02-08 1996-06-21 Transport temperature control system having enhanced low ambient heat capacity

Country Status (5)

Country Link
US (1) US5669223A (no)
CA (1) CA2212640C (no)
NO (1) NO307762B1 (no)
SE (1) SE510736C2 (no)
WO (1) WO1996024809A1 (no)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6095427A (en) * 1999-04-22 2000-08-01 Thermo King Corporation Temperature control system and method for efficiently obtaining and maintaining the temperature in a conditioned space
ES2155745A1 (es) * 1998-04-20 2001-05-16 Samsung Electronics Co Ltd Acondicionador de aire de tipo multiple.
US20030037553A1 (en) * 2001-08-10 2003-02-27 Thermo King Corporation Advanced refrigeration system
US6560978B2 (en) 2000-12-29 2003-05-13 Thermo King Corporation Transport temperature control system having an increased heating capacity and a method of providing the same
US6609382B2 (en) 2001-06-04 2003-08-26 Thermo King Corporation Control method for a self-powered cryogen based refrigeration system
US6631621B2 (en) 2001-07-03 2003-10-14 Thermo King Corporation Cryogenic temperature control apparatus and method
US6679320B2 (en) * 1998-05-28 2004-01-20 Valeo Climatisation Vehicle air conditioning circuit using a refrigerant fluid in the supercritical state
US6694765B1 (en) 2002-07-30 2004-02-24 Thermo King Corporation Method and apparatus for moving air through a heat exchanger
US6698212B2 (en) 2001-07-03 2004-03-02 Thermo King Corporation Cryogenic temperature control apparatus and method
US6751966B2 (en) 2001-05-25 2004-06-22 Thermo King Corporation Hybrid temperature control system
US20040168448A1 (en) * 2003-02-28 2004-09-02 Kadle Prasad Shripad Hvac system with refrigerant venting
US20050066671A1 (en) * 2003-09-26 2005-03-31 Thermo King Corporation Temperature control apparatus and method of operating the same
US20050132735A1 (en) * 2003-12-17 2005-06-23 Yu Chen Transcritical vapor compression optimization through maximization of heating capacity
US20080307824A1 (en) * 2007-06-18 2008-12-18 George John Botich Cooling insert for a container
US20100101770A1 (en) * 2008-10-24 2010-04-29 Thoegersen Ole Controlling chilled state of a cargo
US10107536B2 (en) 2009-12-18 2018-10-23 Carrier Corporation Transport refrigeration system and methods for same to address dynamic conditions
US10533782B2 (en) 2017-02-17 2020-01-14 Keeprite Refrigeration, Inc. Reverse defrost system and methods

Citations (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3370438A (en) * 1966-05-04 1968-02-27 Carrier Corp Condensing pressure controls for refrigeration system
GB2042150A (en) * 1979-02-05 1980-09-17 Carrier Corp Vapour compression refrigeration system and a method of operation therefor
US4226604A (en) * 1979-05-14 1980-10-07 Solar Specialties, Inc. Method and apparatus for preventing overheating of the superheated vapors in a solar heating system using a refrigerant
US4268291A (en) * 1979-10-25 1981-05-19 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4306420A (en) * 1979-10-25 1981-12-22 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4324105A (en) * 1979-10-25 1982-04-13 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4362030A (en) * 1981-09-02 1982-12-07 Carrier Corporation Refrigeration circuit
US4394816A (en) * 1981-11-02 1983-07-26 Carrier Corporation Heat pump system
US4419866A (en) * 1982-06-09 1983-12-13 Thermo King Corporation Transport refrigeration system control
US4454725A (en) * 1982-09-29 1984-06-19 Carrier Corporation Method and apparatus for integrating a supplemental heat source with staged compressors in a heat pump
US4720980A (en) * 1987-03-04 1988-01-26 Thermo King Corporation Method of operating a transport refrigeration system
US4748818A (en) * 1987-06-15 1988-06-07 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
EP0348333A1 (en) * 1988-06-20 1989-12-27 Carrier Corporation Quench expansion valve refrigeration circuit
US4903495A (en) * 1989-02-15 1990-02-27 Thermo King Corp. Transport refrigeration system with secondary condenser and maximum operating pressure expansion valve
US4912933A (en) * 1989-04-14 1990-04-03 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5056324A (en) * 1991-02-21 1991-10-15 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5157933A (en) * 1991-06-27 1992-10-27 Carrier Corporation Transport refrigeration system having means for achieving and maintaining increased heating capacity
US5168713A (en) * 1992-03-12 1992-12-08 Thermo King Corporation Method of operating a compartmentalized transport refrigeration system
US5172559A (en) * 1991-10-31 1992-12-22 Thermo King Corporation Compartmentalized transport refrigeration system having means for enhancing the capacity of a heating cycle
US5193353A (en) * 1991-07-05 1993-03-16 Carrier Corporation High capacity hot gas heating system for transport refrigeration system
US5197297A (en) * 1991-07-29 1993-03-30 Carrier Corporation Transport refrigeration system having compressor over-temperature protection in all operating modes
US5415006A (en) * 1993-11-18 1995-05-16 Thermo King Transport refrigeration unit having means for increasing the amount of refrigerant charge available

Patent Citations (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3370438A (en) * 1966-05-04 1968-02-27 Carrier Corp Condensing pressure controls for refrigeration system
GB2042150A (en) * 1979-02-05 1980-09-17 Carrier Corp Vapour compression refrigeration system and a method of operation therefor
US4258553A (en) * 1979-02-05 1981-03-31 Carrier Corporation Vapor compression refrigeration system and a method of operation therefor
US4226604A (en) * 1979-05-14 1980-10-07 Solar Specialties, Inc. Method and apparatus for preventing overheating of the superheated vapors in a solar heating system using a refrigerant
US4268291A (en) * 1979-10-25 1981-05-19 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4306420A (en) * 1979-10-25 1981-12-22 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4324105A (en) * 1979-10-25 1982-04-13 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4362030A (en) * 1981-09-02 1982-12-07 Carrier Corporation Refrigeration circuit
US4394816A (en) * 1981-11-02 1983-07-26 Carrier Corporation Heat pump system
US4419866A (en) * 1982-06-09 1983-12-13 Thermo King Corporation Transport refrigeration system control
US4454725A (en) * 1982-09-29 1984-06-19 Carrier Corporation Method and apparatus for integrating a supplemental heat source with staged compressors in a heat pump
US4720980A (en) * 1987-03-04 1988-01-26 Thermo King Corporation Method of operating a transport refrigeration system
US4748818A (en) * 1987-06-15 1988-06-07 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
EP0348333A1 (en) * 1988-06-20 1989-12-27 Carrier Corporation Quench expansion valve refrigeration circuit
US4986084A (en) * 1988-06-20 1991-01-22 Carrier Corporation Quench expansion valve refrigeration circuit
US4903495A (en) * 1989-02-15 1990-02-27 Thermo King Corp. Transport refrigeration system with secondary condenser and maximum operating pressure expansion valve
US4912933A (en) * 1989-04-14 1990-04-03 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5056324A (en) * 1991-02-21 1991-10-15 Thermo King Corporation Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5157933A (en) * 1991-06-27 1992-10-27 Carrier Corporation Transport refrigeration system having means for achieving and maintaining increased heating capacity
US5193353A (en) * 1991-07-05 1993-03-16 Carrier Corporation High capacity hot gas heating system for transport refrigeration system
US5197297A (en) * 1991-07-29 1993-03-30 Carrier Corporation Transport refrigeration system having compressor over-temperature protection in all operating modes
US5172559A (en) * 1991-10-31 1992-12-22 Thermo King Corporation Compartmentalized transport refrigeration system having means for enhancing the capacity of a heating cycle
US5168713A (en) * 1992-03-12 1992-12-08 Thermo King Corporation Method of operating a compartmentalized transport refrigeration system
US5415006A (en) * 1993-11-18 1995-05-16 Thermo King Transport refrigeration unit having means for increasing the amount of refrigerant charge available

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2155745A1 (es) * 1998-04-20 2001-05-16 Samsung Electronics Co Ltd Acondicionador de aire de tipo multiple.
US6679320B2 (en) * 1998-05-28 2004-01-20 Valeo Climatisation Vehicle air conditioning circuit using a refrigerant fluid in the supercritical state
US6095427A (en) * 1999-04-22 2000-08-01 Thermo King Corporation Temperature control system and method for efficiently obtaining and maintaining the temperature in a conditioned space
US6560978B2 (en) 2000-12-29 2003-05-13 Thermo King Corporation Transport temperature control system having an increased heating capacity and a method of providing the same
US6751966B2 (en) 2001-05-25 2004-06-22 Thermo King Corporation Hybrid temperature control system
US6609382B2 (en) 2001-06-04 2003-08-26 Thermo King Corporation Control method for a self-powered cryogen based refrigeration system
US6631621B2 (en) 2001-07-03 2003-10-14 Thermo King Corporation Cryogenic temperature control apparatus and method
US6698212B2 (en) 2001-07-03 2004-03-02 Thermo King Corporation Cryogenic temperature control apparatus and method
US6708510B2 (en) 2001-08-10 2004-03-23 Thermo King Corporation Advanced refrigeration system
US20030037553A1 (en) * 2001-08-10 2003-02-27 Thermo King Corporation Advanced refrigeration system
US6694765B1 (en) 2002-07-30 2004-02-24 Thermo King Corporation Method and apparatus for moving air through a heat exchanger
US6907748B2 (en) * 2003-02-28 2005-06-21 Delphi Technologies, Inc. HVAC system with refrigerant venting
US20040168448A1 (en) * 2003-02-28 2004-09-02 Kadle Prasad Shripad Hvac system with refrigerant venting
US20050066671A1 (en) * 2003-09-26 2005-03-31 Thermo King Corporation Temperature control apparatus and method of operating the same
US6910341B2 (en) 2003-09-26 2005-06-28 Thermo King Corporation Temperature control apparatus and method of operating the same
US20050132735A1 (en) * 2003-12-17 2005-06-23 Yu Chen Transcritical vapor compression optimization through maximization of heating capacity
WO2005059448A3 (en) * 2003-12-17 2005-11-10 Carrier Corp Transcritical vapor compression optimization through maximization of heating capacity
US7051542B2 (en) * 2003-12-17 2006-05-30 Carrier Corporation Transcritical vapor compression optimization through maximization of heating capacity
US20080307824A1 (en) * 2007-06-18 2008-12-18 George John Botich Cooling insert for a container
US20100101770A1 (en) * 2008-10-24 2010-04-29 Thoegersen Ole Controlling chilled state of a cargo
US8607582B2 (en) * 2008-10-24 2013-12-17 Thermo King Corporation Controlling chilled state of a cargo
US8800307B2 (en) 2008-10-24 2014-08-12 Thermo King Corporation Controlling chilled state of a cargo
US9857114B2 (en) 2008-10-24 2018-01-02 Thermo King Corporation Controlling chilled state of a cargo
US10619902B2 (en) 2008-10-24 2020-04-14 Thermo King Corporation Controlling chilled state of a cargo
US10107536B2 (en) 2009-12-18 2018-10-23 Carrier Corporation Transport refrigeration system and methods for same to address dynamic conditions
US10533782B2 (en) 2017-02-17 2020-01-14 Keeprite Refrigeration, Inc. Reverse defrost system and methods

Also Published As

Publication number Publication date
NO973570L (no) 1997-10-06
CA2212640C (en) 2002-11-26
CA2212640A1 (en) 1996-08-15
SE9702875D0 (sv) 1997-08-06
SE9702875L (sv) 1997-10-08
SE510736C2 (sv) 1999-06-21
NO307762B1 (no) 2000-05-22
WO1996024809A1 (en) 1996-08-15
NO973570D0 (no) 1997-08-04

Similar Documents

Publication Publication Date Title
US5669223A (en) Transport temperature control system having enhanced low ambient heat capacity
US4903495A (en) Transport refrigeration system with secondary condenser and maximum operating pressure expansion valve
US4770000A (en) Defrosting of refrigerator system out-door heat exchanger
US4644756A (en) Multi-room type air conditioner
US5410889A (en) Methods and apparatus for operating a refrigeration system
EP0392673B1 (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5400609A (en) Methods and apparatus for operating a refrigeration system characterized by controlling maximum operating pressure
US5477695A (en) Methods and apparatus for operating a refrigeration system characterized by controlling engine coolant
US5056324A (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
US5197297A (en) Transport refrigeration system having compressor over-temperature protection in all operating modes
EP0295894B1 (en) Transport refrigeration system having means for enhancing the capacity of a heating cycle
JPH05231724A (ja) 冷凍装置及びその作動方法
KR950007280B1 (ko) 다중형 공기 조화기
EP0470238A1 (en) Hot gas defrost refrigeration system
EP0407328A2 (en) Unloading system for two-stage compressors
JPH05223384A (ja) ヒート・ポンプ系
JPH05272817A (ja) 空調装置
JPH0135269B2 (no)
US4327558A (en) Unloadable transport refrigeration unit control
JP4898025B2 (ja) マルチ型ガスヒートポンプ式空気調和装置
US5107686A (en) Compartmentalized transport refrigeration system
JPH07294026A (ja) 冷凍装置
JPH08276727A (ja) 車両用空気調和装置
JPS61159072A (ja) 冷凍装置
JP3242221B2 (ja) 空気調和機

Legal Events

Date Code Title Description
FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

FPAY Fee payment

Year of fee payment: 4

REMI Maintenance fee reminder mailed
FPAY Fee payment

Year of fee payment: 8

SULP Surcharge for late payment

Year of fee payment: 7

REMI Maintenance fee reminder mailed
LAPS Lapse for failure to pay maintenance fees
STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20090923